JP3665330B2 - Drive connector - Google Patents

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JP3665330B2
JP3665330B2 JP51556391A JP51556391A JP3665330B2 JP 3665330 B2 JP3665330 B2 JP 3665330B2 JP 51556391 A JP51556391 A JP 51556391A JP 51556391 A JP51556391 A JP 51556391A JP 3665330 B2 JP3665330 B2 JP 3665330B2
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Prior art keywords
shaft
drive connector
drive shaft
slider
connector according
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JPH06502466A (en
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ミッチェル，ウティーヴン・ウィリアム
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メカダイン・インターナショナル・リミテッド
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Transmission Devices (AREA)
  • Manipulator (AREA)

Description

【０００１】
【産業上の技術分野】
本発明は、互いに平行である回転軸線をそれぞれ有する第１の回転体及び第２の回転体を備え、一方の回転軸線が他方の回転軸線に関してその回転軸線に直交する方向に移動可能であり、第１の回転体が中空で、第２の回転体が第１の回転体内に配置された、二つの回転体間の駆動接続具に関する。本発明は、特に、二つの回転体が共にシャフトであり、第１の回転体が中空シャフトであり、多分、中実で組み合わせ体の駆動部材である第２の回転体が第１の回転体の内部に配置された駆動接続具に関する。
【０００２】
【背景技術】
本発明は、英国特許２０６６３６１号及び同第２２０６１７９号の明細書に記載された型式の機構に関し、その機構は、内燃機関の弁を作動させ、作動状態の変化に適合するように作動中の弁のタイミングを変化させることができる。また、この機構において、中空のシャフトが該中空のシャフト内に配置された中実なシャフトによって駆動される。
【０００３】
例えば、一例として、英国特許第２０６６３６１号の明細書に記載された駆動シャフトとカムシャフトとの間の接続具は、インライン形シリンダを備えるが該シリンダの吸気弁がそのラインに対して排気弁からオフセットされているエンジンに、適している。英国特許第２２０６１７９号の明細書に基づく発明は、シリンダがインライン形であり、吸気弁及び排気弁もまた、シリンダの中心と一直線であるコンパクトなエンジンで使用することの出来る機構が必要とされることに起因する。該発明の別のファクタは、英国特許第２０６６３６１号におけるように、弁作動カムがロッカー又はレバーにではなく、バケットタペットに、直接作用するようにすることが益々、望まれることである。
【０００４】
一例として、英国特許第２２０６１７９号の明細書に記載された設計において、中央の駆動シャフトとその駆動シャフトを囲繞する中空のカムシャフトとの間の駆動接続具は、一例として、駆動シャフトから半径方向に突出するアームによって形成される。該アームの外端は、その軸線が駆動シャフトの軸線に対し平行になっている一部円筒形の形状をしている。その外端は一部円形の形状をしており、この外端は、中空のカムシャフトに取り付けたフランジに形成した半径方向スロット内を摺動可能に取り付けたブロックに形成される対応する凹所に回転可能に係合する。かかる接続具は、上述の全ての構成要素が、英国特許第２０６６３６１号、及び欧州特許第０１７９５８１号の接続具と異なり、駆動シャフト及び駆動シャフトの回転軸線に対し同一の横断面内に位置するため、軸方向に極めてコンパクトであるという利点が得られる。上記両特許において、二つのシャフトの間の駆動接続具内には、ピン等により接続される軸方向空隙がある。
【０００５】
【発明が解決しようとする課題】
本発明は、英国特許第２２０６１７９号の設計の軸方向へのコンパクトさに加えて、半径方向にも著しくコンパクトであり、特に、駆動シャフトの回転軸線と回転継手の回転中心との間の距離（半径）Ｙを縮小させることの利益を認識することにより為されたものである。かかる駆動接続具の場合、弁のタイミングの実現可能な可変範囲は、Ｘ／Ｙの関数に比例し、ここで、Ｘは、駆動シャフトの回転軸線と被動シャフトの回転軸線との間の距離であり、Ｙは、上述の通りである。あらゆる実用的な設計において、Ｘの最大量は、被駆動側の中空のカムシャフトのボアによって制限される。その理由は、その寸法が少しでも増大することは、中空のカムシャフトの軸受けにおける摩擦損失を増大させ、又、これに比例して、カムベースの円形の直径を大きくしなければならないため、被動カム（カムフォロア）の表面における表面速度及び摩擦損失を増大させる傾向となるからである。故に、Ｙの値を最小にすることにより、Ｘ／Ｙの関数の値を最大にすることが有利である。
【０００６】
【課題を解決するための手段】
本発明は、本発明の開示範囲に含まれるべき開示内容の請求の範囲によって規定される。
【０００７】
本発明は、又、一例として、添付図面に関して説明する駆動接続具及び弁タイミング機構を含むものである。
【０００８】
【発明の実施の形態】
符号２で示す少なくとも一つの弁作動カムを支持する中空のカムシャフト１は、固定の回転軸線３の周りを回転し、典型的に、チェーン７を介してエンジンのクランクシャフト６から駆動される中実な駆動シャフト５により、全体として符号４で示した駆動接続具を介して駆動され、このチェーン７及びクランクシャフト６は、第２図に概略図でのみ示してある。駆動シャフト５の回転軸線８は、常にカムシャフト１の回転軸線３に対して平行である。図１において、二つの回転軸線は一致するが、駆動シャフト５に応答してカムシャフト１の回転パターンを変化させ、これにより、カム２によりエンジンの弁の開閉タイミングを変化させるべく、例えば、符号９で概略図でのみ示されかつ当該技術分野で周知の型式である、英国特許第２０６６３６１号の明細書に記載された機構によって回転軸線８をその軸線に直角の方向に動かすことができる。
【０００９】
カムシャフト１は、半径方向スロット１１が形成されたフランジ１０を支持し、該スロット１１内には、スライダ１２が摺動可能に取り付けられる。スライダ１２には、一部円筒状のキャビティ１３が形成され、そのキャビティ１３の軸線は、回転軸線３、８に対して平行に位置する。スライダ１２の軸線に沿った方向の長さ（又は厚さ）に対応する軸方向長さ（又は厚さ）を有していてそのキャビティに合う一部円筒状の部材１５は、スライダ１２のキャビティ１３に等しい半径（１７）を有する凸状面領域１６を提供し、このため、スライダ１２及び部材１５は、凸状面の曲率中心すなわち回転軸線１８を有する回転継手の二つの半体として機能する。部材１５の凹状面領域１９の曲率は、駆動シャフト５の表面に適合し且つ該面と整合する。図１及び図２に図示した例において、駆動シャフト５及び部材１５は、ソケットヘッドキャップねじ２１により共に保持されかつ中空の位置決め止め部材２２により相互に位置決めされる。別の実施例において、部材１５は、例えば、リベットによって駆動シャフト５に一層恒久的に固定することができ、又は駆動シャフト５と一体に形成することも可能である。
【００１０】
図１の主要部分のうち、駆動シャフト５及び部材１５の組み合わせは、駆動シャフトの回転軸線８の周りを回転可能な一つのアームを形成することが明らかである。アームがその一部である駆動機構は、英国特許第２２０６１７９号の明細書に記載された連結機構と略同一の方法にて、回転軸線３と回転軸線８との間の距離の変化に伴って、カムシャフト１に付与される回転パターンを変化させることができる。駆動シャフト５の外周には、スライダ１２の付近に小さい切欠き２３が形成されており、該切欠き２３は、回転軸線３と回転軸線８との間の距離が最大程度に達するのに伴って、各回転中、スライダが駆動シャフト５に対して為す傾動動作を許容する隙間を提供する。図１には、上述のアームの断面積が駆動シャフト５及び部材１５の断面積の合計値に略等しい、本発明の特徴が示されている。部材１５の表面領域１６、１９の凸形及び凹形の形状の結果、回転軸線８と曲率中心（回転中心でもある）１８との間の距離２４（前述の距離Ｙに対応する）が短くなる。これは、関数Ｘ／Ｙの値を小さくするのに有効であり、上述の効果及び利点が得られる。図１に図示するように、部材１５をそのような構造及び取り付け状態としたとき、回転継手の回転中心１８は、その軸線に沿って見たとき、駆動シャフト５の外周の輪郭内に位置し、回転中心１８と回転軸線８との間の距離は、駆動シャフト５の半径よりも短くなる。かかる小さい値は、英国特許第２２０６１７９号の明細書に一例として掲げた何れの構造体においても全く実現不可能であり、その英国特許における駆動部材（２）の形状が全く異なる結果、駆動シャフトの回転軸線（２０）と回転継手の曲率中心（３３）との間の距離は、常に駆動シャフトの半径を上廻るものでなければならない。
【００１１】
駆動シャフト５及び部材１５が一体である上述の本発明の別の実施例において、図１の凹状面１９に対応する駆動シャフトと部材との間の想定上の境界は、勿論、駆動シャフトの外周の想定上の投影像によって決まる。図示するように、駆動シャフトが円形断面である場合、その外周も円形となるが、本発明は、駆動シャフトが非円形の外形である機構を備え、駆動シャフトと部材１５との間の実際的、又は想定上の境界は、かかる非円形の外形の投影像である。
【００１２】
図３及び図４の別の構造において、部材１５ａは、図１及び図２の対応する部材１５のような三日月状の断面形状ではなく、外周３０と、駆動シャフト５に形成された横方向スロット３３の底部３２に係合する弦３１で境界を画成する不完全な円の断面形状をしている。前の図面と同様に、駆動シャフト及び部材１５ａは、位置決め部材２２及びねじ２１により配置され且つ相互に保持される。部材１５ａの外周３０は、前と同様に回転継手用の必要な凸状面（１６）を提供し、回転中心１８と回転軸線８との間の距離も同様に、駆動シャフト５の半径よりも短い。また、図３に断面図で示すように、回転継手の構成要素（駆動シャフト５及び部材１５ａ）の形状は、図１の同様の断面図に示す対応する構成要素（５、１５）の形状とは異なるが、これら二つの構成要素の組み合わせにより形成される「アーム」の断面積は、前と同様に、これら二つの部分の合計値に等しい。これらの部分の第一の部分は、駆動シャフト５の外周内に包み込まれた駆動シャフト５の断面であり、参照符号３４は、部材１５ａによってその外周が不鮮明にされる輪郭の連続部分を示す。該面積の第二の部分は、図１におけるように半月状の形状であり、一側部で外周３０（１６）と、及び反対側の側部で線３４と境界を接している。
【００１３】
最後に、実際には、第１図及び第３図に図示するように、部材１５、１５ａの半径はシャフト５の半径に等しくするのは都合がよいことが多いが、本発明は、部材がスライダと共に形成する回転継手の回転半径よりも円形の駆動シャフトの半径の方が大きいか、又は小さい駆動接続具をも包含するものである。
【図面の簡単な説明】
図１は、駆動シャフト及び被駆動のカムシャフト、並びにこれらシャフト間の駆動接続具の横断面図、
図２は、図１の矢印IIの方向の平面図、
図３は、別の構造体の横断面図の詳細図、
図４は、図３の駆動シャフトの立面図である。[0001]
[Industrial technical field]
The present invention includes a first rotating body and a second rotating body each having a rotation axis parallel to each other, and one rotation axis is movable in a direction perpendicular to the rotation axis with respect to the other rotation axis, The present invention relates to a drive connection tool between two rotating bodies, in which the first rotating body is hollow and the second rotating body is arranged in the first rotating body. In particular, the present invention provides that the two rotating bodies are both shafts, the first rotating body is a hollow shaft, and the second rotating body, which is probably a solid and combined drive member, is the first rotating body. It relates to the drive connector arrange | positioned inside.
[0002]
[Background]
The present invention relates to a mechanism of the type described in GB 2066361 and 2206179, which actuates a valve of an internal combustion engine and is in operation to adapt to changes in operating conditions. The timing can be changed . In this mechanism, the hollow shaft is driven by a solid shaft disposed in the hollow shaft.
[0003]
For example, as an example, the connection between the drive shaft and camshaft described in GB 2066361 includes an inline cylinder, where the intake valve of the cylinder is connected to the line from the exhaust valve. the engine being offset, are suitable. The invention based on GB 2206179 requires a mechanism that can be used in a compact engine in which the cylinder is in-line and the intake and exhaust valves are also in line with the center of the cylinder. Due to that. Another factor of the invention is the increasing desirability of having the valve actuating cam act directly on the bucket tappet rather than on the rocker or lever as in GB 2066361.
[0004]
As an example, in design described in the specification of British Patent No. 2206179, a driving connector between the hollow camshaft that surrounds the central drive shaft and a driving shaft, by way of example, radially from the drive shaft Formed by an arm projecting into The outer end of the arm has a partially cylindrical shape whose axis is parallel to the axis of the drive shaft. Its outer end is partly circular in shape and this outer end is a corresponding recess formed in a block slidably mounted in a radial slot formed in a flange attached to a hollow camshaft. To be rotatably engaged. Such a connector is different from the connectors of British Patent No. 2066361 and European Patent No. 0179581, because all the above-mentioned components are located in the same cross section with respect to the rotation axis of the drive shaft and the drive shaft. The advantage of being extremely compact in the axial direction is obtained. In both of the above patents, there is an axial gap connected by a pin or the like in the drive connection between the two shafts .
[0005]
[Problems to be solved by the invention]
In addition to the axial compactness of the design of GB 2206179, the present invention is also extremely compact in the radial direction, in particular the distance between the rotational axis of the drive shaft and the rotational center of the rotary joint ( (Radius) is done by recognizing the benefits of reducing Y. For such drive connector, feasible variable range of the timing of the valve is proportional to a function of X / Y, where, X is the distance between the axis of rotation of the rotational axis and the driven shaft of the drive shaft Yes, Y is as described above. In any practical design, the maximum amount of X is limited by the bore of the driven hollow camshaft. The reason is that the size increases even slightly increases the friction losses in the bearings of the hollow camshaft, also, that in proportion to this, it is necessary to increase the diameter of the circular cam base, the driven This is because the surface speed and friction loss on the surface of the cam (cam follower) tend to increase. Therefore, it is advantageous to maximize the value of the X / Y function by minimizing the value of Y.
[0006]
[Means for Solving the Problems]
The present invention is defined by the claims of the disclosure to be included in the disclosure scope of the present invention.
[0007]
The present invention also includes, by way of example, drive fittings and valve timing mechanisms described with reference to the accompanying drawings.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hollow cam shaft 1 which supports at least one valve operating cam indicated at 2, rotates about a rotational axis 3 of the fixed, typically in driven from the crankshaft 6 of the engine through a chain 7 The chain 7 and the crankshaft 6 are shown in schematic form only in FIG. 2 by being driven by a real drive shaft 5 as a whole via the drive connection indicated by reference numeral 4. The rotational axis 8 of the drive shaft 5 is always parallel to the rotational axis 3 of the camshaft 1. In Figure 1, the two rotating axis coincides, in response to a drive shaft 5 to change the rotation pattern of the cam shaft 1, thereby to vary the opening and closing timing of a valve of the engine by the cam 2, for example, code The axis of rotation 8 can be moved in a direction perpendicular to the axis by means of the mechanism described in GB 2066361 , which is only shown schematically in FIG. 9 and is of the type well known in the art .
[0009]
The camshaft 1 supports a flange 10 in which a radial slot 11 is formed, and a slider 12 is slidably mounted in the slot 11. The slider 12 is formed with a partially cylindrical cavity 13, and the axis of the cavity 13 is positioned in parallel to the rotation axes 3 and 8. Axial length (or thickness) have a part cylindrical member 15 that fits the cavity corresponding to the direction of the length (or thickness) along the axis of the slider 12, the cavity of the slider 12 A convex surface area 16 having a radius (17) equal to 13 is provided, so that the slider 12 and the member 15 function as two halves of a rotary joint having a center of curvature of the convex surface, ie the axis of rotation 18. . The curvature of the concave surface area 19 of the member 15 matches the surface of the drive shaft 5 and matches it. In the example illustrated in FIGS. 1 and 2, the drive shaft 5 and the member 15 are held together by a socket head cap screw 21 and are positioned relative to each other by a hollow positioning stop member 22. In another embodiment, the member 15 can be more permanently fixed to the drive shaft 5 by, for example, rivets, or can be formed integrally with the drive shaft 5.
[0010]
Of the main parts of FIG. 1, it is apparent that the combination of the drive shaft 5 and the member 15 forms one arm that can rotate about the rotation axis 8 of the drive shaft. Drive mechanism arm is a part, at GB 2206179 No. specification has been linked mechanisms substantially the same manner described, with a change of the distance between the rotation axis 3 and axis of rotation 8 , Ru can be changed rotation pattern imparted to the camshaft 1. The outer periphery of the drive shaft 5, a small notch 23 in the vicinity of the slider 12 and is formed, notch 23, as the distance between the rotation axis 3 and the rotary axis 8 reaches the maximum of about Provide a gap allowing the tilting action of the slider relative to the drive shaft 5 during each rotation. FIG. 1 shows a feature of the present invention in which the cross-sectional area of the arm described above is approximately equal to the sum of the cross-sectional areas of the drive shaft 5 and the member 15. As a result of the convex and concave shapes of the surface regions 16 and 19 of the member 15, the distance 24 (corresponding to the above-mentioned distance Y) between the rotation axis 8 and the center of curvature (which is also the rotation center) 18 is shortened. . This is effective for reducing the value of the function X / Y, and the above-described effects and advantages are obtained. As shown in FIG. 1, when the member 15 is in such a structure and attached state, the rotation center 18 of the rotary joint is positioned within the contour of the outer periphery of the drive shaft 5 when viewed along its axis. The distance between the rotation center 18 and the rotation axis 8 is shorter than the radius of the drive shaft 5. Such a small value is not feasible in any structure listed as an example in the specification of British Patent No. 2206179, and the shape of the drive member (2) in that British patent is quite different, resulting in the drive shaft The distance between the axis of rotation (20) and the center of curvature (33) of the rotary joint must always exceed the radius of the drive shaft.
[0011]
Drive shaft 5 and member 15 are integral in another embodiment of the present invention described above, assuming the boundary between the drive shaft and the member corresponding to the concave surface 19 of Figure 1 is, of course, the outer periphery of the drive shaft It depends on the projected image. As shown in the figure, when the drive shaft has a circular cross section, the outer periphery thereof is also circular. However, the present invention includes a mechanism in which the drive shaft has a non-circular outer shape, and the drive shaft and the member 15 are practically provided. Or the hypothetical boundary is a projected image of such a non-circular contour.
[0012]
3 and 4, the member 15 a is not a crescent-shaped cross-section like the corresponding member 15 of FIGS. 1 and 2, but a lateral slot formed in the outer periphery 30 and the drive shaft 5. The chord 31 that engages the bottom 32 of the 33 has an incomplete circular cross-sectional shape that defines a boundary. Similar to the previous drawing, the drive shaft and member 15a are arranged and held together by positioning member 22 and screw 21. Periphery 30 of member 15a is before and provides the necessary convex surface of the rotary joint as well (16), as well the distance between the rotation center 18 and the axis of rotation 8, than the radius of the drive shaft 5 short. Further, as shown in the sectional view of FIG. 3, the shape of the components ( drive shaft 5 and member 15a) of the rotary joint is the same as the shape of the corresponding components (5, 15) shown in the same sectional view of FIG. The cross-sectional area of the “arm” formed by the combination of these two components is equal to the sum of these two parts , as before. The first of these parts is a cross section of the drive shaft 5 encased in an outer periphery of the drive shaft 5, reference numeral 34 indicates a continuous portion of the contour its periphery is blurred by the member 15a. The second part of the area has a half-moon shape as in FIG. 1 and borders the outer circumference 30 (16) on one side and the line 34 on the opposite side.
[0013]
Finally, in practice, as shown in Figure 1 and Figure 3, the radius of the member 15,15a is often better convenience to equal the radius of the shaft 5, the present invention is member It also includes a drive connector in which the radius of the circular drive shaft is larger or smaller than the radius of rotation of the rotary joint formed with the slider.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a drive shaft and a driven camshaft, and a drive connection between these shafts,
2 is a plan view in the direction of arrow II in FIG.
FIG. 3 is a detailed view of a cross-sectional view of another structure,
4 is an elevational view of the drive shaft of FIG.

Claims (7)

互いに平行であるそれぞれの回転軸線（３、８）の回りで回転可能な第１及び第２のシャフト（１、５）を互いに接続するための駆動接続具であって、前記第１のシャフトが中空であり、前記第２のシャフトが前記第１のシャフト内に配置され、前記第２のシャフトの回転軸線が前記第１のシャフトの回転軸線に関して半径方向に移動可能で前記二つの回転軸線間の距離を変更でき、前記駆動接続具が前記第１のシャフトに形成されかつ半径方向に伸びる摺動路と、前記摺動路内でその摺動路に沿って半径方向に移動可能なスライダ（１２）と、前記スライダが前記第２のシャフトに関して回動できるように前記スライダを前記第２のシャフトに接続する回転継手とを備えた駆動接続具において、前記第２のシャフトの回転軸線からの前記回転継手の回転軸線までの距離が前記第２のシャフトの半径より小さいことを特徴とする駆動接続具。 A drive connector for connecting the first and second shafts (1, 5) rotatable about respective rotation axes (3, 8) parallel to each other, the first shaft comprising: It is hollow, the second shaft is disposed in the first shaft, the rotation axis of the second shaft is movable in a radial direction with respect to the rotation axis of the first shaft, and is between the two rotation axes. A sliding path that is formed on the first shaft and extends in the radial direction, and a slider that is movable in the sliding path in the radial direction along the sliding path. 12), and a rotary joint that connects the slider to the second shaft so that the slider can rotate with respect to the second shaft. Times Drive connector that distance to the rotation axis of the joint is smaller than a radius of the second shaft. 請求項１に記載の駆動接続具において、前記回転継手が、前記第２のシャフトと共に回転しかつ前記スライダに形成された曲面と接触する曲面を有する一部円形の部材（１５、１５ａ）を有する駆動接続具。The drive connector according to claim 1, wherein the rotary joint includes a partially circular member (15, 15a) having a curved surface that rotates with the second shaft and contacts a curved surface formed on the slider. Driving connector. 請求項２に記載の駆動接続具において、前記一部円形の部材が前記第２のシャフトと一体的に形成されている駆動接続具。 The drive connector according to claim 2, wherein the partly circular member is formed integrally with the second shaft . 請求項２に記載の駆動接続具において、前記一部円形の部材が前記第２のシャフトと別体に形成されているがその第２のシャフトに固定されている駆動接続具。 The drive connector according to claim 2, wherein the partially circular member is formed separately from the second shaft, but is fixed to the second shaft . 請求項４に記載の駆動接続具において、前記第２のシャフトは、前記一部円形の部材を受けるスロットを有する駆動接続具。 5. The drive connector according to claim 4, wherein the second shaft has a slot for receiving the partially circular member . 請求項４に記載の駆動接続具において、前記一部円形の部材が三日月形を有し、円形の断面を有する前記第２のシャフトの外周面に固定されている駆動接続具。 5. The drive connector according to claim 4, wherein the partially circular member has a crescent shape and is fixed to an outer peripheral surface of the second shaft having a circular cross section . クランクシャフトとカムシャフトとを有する内燃機関用の弁タイミング機構において、請求項１ないし６の何れかに記載の駆動接続具を備え、前記駆動接続具の第２のシャフトが前記クランクシャフトによって回転され、前記駆動接続具の前記第１のシャフトが前記カムシャフトを構成することを特徴とする弁タイミング機構。A valve timing mechanism for an internal combustion engine having a crankshaft and a camshaft, comprising the drive connector according to any one of claims 1 to 6, wherein a second shaft of the drive connector is rotated by the crankshaft. The valve timing mechanism is characterized in that the first shaft of the drive connector constitutes the camshaft.
JP51556391A 1990-10-01 1991-09-30 Drive connector Expired - Fee Related JP3665330B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9021270.5 1990-10-01
GB909021270A GB9021270D0 (en) 1990-10-01 1990-10-01 Improvements in or relating to driving connections between two rotatable bodies
PCT/GB1991/001680 WO1992006282A1 (en) 1990-10-01 1991-09-30 Improvements in or relating to driving connections between two rotatable bodies

Publications (2)

Publication Number Publication Date
JPH06502466A JPH06502466A (en) 1994-03-17
JP3665330B2 true JP3665330B2 (en) 2005-06-29

Family

ID=10683013

Family Applications (1)

Application Number Title Priority Date Filing Date
JP51556391A Expired - Fee Related JP3665330B2 (en) 1990-10-01 1991-09-30 Drive connector

Country Status (10)

Country Link
US (1) US5417611A (en)
EP (1) EP0551339B1 (en)
JP (1) JP3665330B2 (en)
CA (1) CA2093117C (en)
DE (1) DE69112071T2 (en)
ES (1) ES2077868T3 (en)
GB (2) GB9021270D0 (en)
IN (1) IN184840B (en)
RU (1) RU2068102C1 (en)
WO (1) WO1992006282A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5738055A (en) * 1996-10-23 1998-04-14 Cloyes Gear And Products, Inc. Adjustable camshaft timing device
GB2365508A (en) * 2000-08-08 2002-02-20 Mechadyne Internat Plc Variable valve timing mechanism
US7104229B2 (en) * 2001-04-05 2006-09-12 Stephen William Mitchell Variable valve timing system
GB0512161D0 (en) 2005-06-14 2005-07-20 Hoover Ltd Vacuum cleaner
DE102007037232A1 (en) * 2007-08-07 2009-02-12 Eto Magnetic Gmbh Device for adjusting the camshaft of an internal combustion engine
SE534761C2 (en) * 2010-04-19 2011-12-13 Scania Cv Ab Valve lift device of an internal combustion engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3010339A (en) * 1958-03-17 1961-11-28 Densmore Richard M Cam mechanical movement
US3491604A (en) * 1968-02-12 1970-01-27 Cass B Levi Device for modifying rotary motion
GB1522405A (en) * 1976-04-02 1978-08-23 Mitchell S Valve timing mechanisms
GB2066361B (en) * 1980-01-02 1984-07-11 Nat Res Dev Valve timing mechanisms of internal combustion engines
IN155023B (en) * 1980-01-02 1984-12-22 Nat Res Dev
GB2165885B (en) * 1984-10-20 1987-12-23 Austin Rover Group I c engine variable valve timing mechanism
GB8711366D0 (en) * 1987-05-14 1987-06-17 Mitchell S W Driving connections between two rotatable bodies

Also Published As

Publication number Publication date
CA2093117A1 (en) 1992-04-02
EP0551339A1 (en) 1993-07-21
EP0551339B1 (en) 1995-08-09
DE69112071T2 (en) 1996-01-11
CA2093117C (en) 2001-07-17
IN184840B (en) 2000-09-30
RU2068102C1 (en) 1996-10-20
ES2077868T3 (en) 1995-12-01
GB2248483A (en) 1992-04-08
JPH06502466A (en) 1994-03-17
US5417611A (en) 1995-05-23
GB9021270D0 (en) 1990-11-14
GB2248483B (en) 1994-03-16
WO1992006282A1 (en) 1992-04-16
DE69112071D1 (en) 1995-09-14
GB9120699D0 (en) 1991-11-13

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